CN102425872B - Refrigeration cycle device - Google Patents
Refrigeration cycle device Download PDFInfo
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- CN102425872B CN102425872B CN201110289736.1A CN201110289736A CN102425872B CN 102425872 B CN102425872 B CN 102425872B CN 201110289736 A CN201110289736 A CN 201110289736A CN 102425872 B CN102425872 B CN 102425872B
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- 238000005057 refrigeration Methods 0.000 title 1
- 239000003507 refrigerant Substances 0.000 claims abstract description 40
- 238000001514 detection method Methods 0.000 claims abstract description 15
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 102
- 238000007710 freezing Methods 0.000 claims description 31
- 230000008014 freezing Effects 0.000 claims description 31
- 238000010438 heat treatment Methods 0.000 claims description 16
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 6
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 3
- 239000001569 carbon dioxide Substances 0.000 claims description 3
- 239000006096 absorbing agent Substances 0.000 abstract 2
- 230000006837 decompression Effects 0.000 abstract 2
- 239000012530 fluid Substances 0.000 description 5
- 238000001704 evaporation Methods 0.000 description 4
- 238000004781 supercooling Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 3
- 239000002826 coolant Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 230000000306 recurrent effect Effects 0.000 description 3
- 239000008400 supply water Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/063—Feed forward expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/17—Control issues by controlling the pressure of the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2102—Temperatures at the outlet of the gas cooler
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
Abstract
A refrigerant cycle apparatus comprising: a compressor 1, a radiator 2, decompression means 3, a heat absorber 4, an internal heat exchanger 5 that performs heat exchange between a refrigerant at an outlet of said radiator and the refrigerant at an outlet of said heat absorber, wherein first temperature detection means 30 for detecting a refrigerant temperature between an outlet of the compressor 1 and an inlet of the radiator 2 and second temperature detection means 31 for detecting the refrigerant temperature between the outlet of the radiator 2 and a high-pressure side inlet of the internal heat exchanger 5 are provided, and an opening degree of decompression means 3 is controlled so that a temperature difference ( T) between a detection temperature by the first temperature detection means 30 and the detection temperature by the second temperature detection means 31 becomes a target value.
Description
The application's denomination of invention that to be Mitsubishi Electric Corporation proposed on 04 29th, 2010 is the divisional application of " freezing cycle device ", the application number application that is 200880114114.1.
Technical field
The present invention relates to use the freezing cycle device of inner heat exchanger, particularly relate to the cold-producing medium control for stably guaranteeing performance.
Background technology
Conventional example is described below.
In the past, as the hot-water supply that freezing cycle device is housed, for example proposing (for example has such hot-water supply, with reference to patent documentation 1), " this hot-water supply has the circulation of refrigerant circulation and supplying hot water, and this refrigerant circulation is by compressor, for supplying hot water, heat exchanger, electric expansion valve and gas is thermal source in addition heat source side heat exchanger form; This supplying hot water circulation is made up of with heat exchanger and heat supply water tank supply-water pump, supplying hot water; Wherein: the compressor that uses ability variable type, simultaneously, set up the capability control unit that carries out the capability control of compressor corresponding to the variation of the external environment condition of heat source side heat exchanger, in addition, set up expansion valve opening control module and rotary speed controling unit; This expansion valve opening control module for example,, corresponding to the variation of the external environment condition (, outer temperature degree) of heat source side heat exchanger, carries out the aperture control of electric expansion valve so that the discharge temperature of compressor becomes the mode of desired value; This rotary speed controling unit, corresponding to the variation of the external environment condition of heat source side heat exchanger, is controlled so that the rotating speed of compressor becomes the mode of desired value; Due to the external environment condition corresponding to heat source side heat exchanger (for example, outer temperature degree) variation so that the discharge temperature of compressor becomes the aperture of the mode control electric expansion valve of desired value, simultaneously, corresponding to the variation of the external environment condition of heat source side heat exchanger so that the rotating speed of compressor becomes the mode of desired value controls, so, can obtain supplying hot water ability and the supplying hot water best running state of more mating of loading, can improve coefficient of refrigerating performance (COP), meanwhile, can make the miniaturization of components of heat exchanger etc.. ".
In addition, proposition (for example has such hot water supply device, with reference to patent documentation 2), " this hot water supply device uses the overcritical heat pump cycle heating supplying hot water fluid of on high-tension side refrigerant pressure more than cold-producing medium critical pressure, it is characterized in that: have compressor, radiator, pressure reducer, evaporimeter; This radiator make from compressor discharge cold-producing medium and supplying hot water fluid carry out heat exchange, and so that flow of refrigerant and supplying hot water with fluid mobile phase to mode form; This pressure reducer reduces pressure to the cold-producing medium flowing out from radiator; This evaporimeter makes the cold-producing medium evaporation of flowing out from pressure reducer, makes cold-producing medium absorb heat, and cold-producing medium is flowed out towards the suction side of compressor; So that the cold-producing medium flowing out from radiator with flow into the temperature difference of fluid for the supplying hot water of radiator (Δ T) and become the on high-tension side refrigerant pressure of mode control of the regulation temperature difference (Δ To) ".In the prior art example, can improve the heat exchanger effectiveness of radiator, the efficiency of raising heat pump.
Patent documentation 1: No. 3601369 communique of Japan Patent (the 6th page, Fig. 1)
Patent documentation 2: No. 3227651 communique of Japan Patent (1-3 page, Fig. 2)
Summary of the invention
In 2 prior art examples shown in above-mentioned, be all so that the discharge temperature of compressor or the cold-producing medium that flows out from radiator with flow into the temperature difference of fluid for the supplying hot water of radiator (Δ T) and become the mode control refrigerant condition of desired value, the running that implementation efficiency is good, but there is such problem, , become near maximum in the efficiency (COP) of freeze cycle, in the control of the outlet side (above-mentioned temperature difference T) of the entrance side based on radiator (above-mentioned discharge temperature) or radiator only, the variation of discharge temperature or temperature difference T is little, be difficult to stably control the operating condition good into efficiency.In addition, also there is such problem, that is, do not consider the action of the occasion that has inner heat exchanger in refrigerant loop, so, be difficult to stably control the operating condition good into efficiency.
The present invention makes in order to solve the problem of prior art as described above, its object is to obtain such freezing cycle device, this freezing cycle device is desired value by the operation values control of the normal condition based on radiator and radiator outlet state, thus the good operating condition of implementation efficiency stably.
In order to solve problem as described above, freezing cycle device of the present invention at least comprises decompressing unit, heat dump, the inner heat exchanger that compressor, radiator, aperture can change, and this inner heat exchanger makes the cold-producing medium of radiator outlet portion and the cold-producing medium of heat dump export department carry out heat exchange; It is characterized in that: at least there is the first refrigerant condition detecting unit of the normal condition that detects radiator and detect the second refrigerant state detection unit from the refrigerant condition between the high-pressure side entrance that exports to inner heat exchanger of radiator, so that become the aperture of the mode control decompressing unit of desired value according to the operation values of the output computing of the output of the first refrigerant condition detecting unit and second refrigerant state detection unit.
The effect of invention
In the present invention, according to the refrigerant condition of the normal condition of radiator and radiator outlet portion so that the mode control expansion valve opening of COP maximum, so, can obtain the freezing cycle device of stably realizing high efficiency running.
Brief description of the drawings
Fig. 1 is the figure that represents the formation of the freezing cycle device of embodiment of the present invention 1.
Fig. 2 is the figure that represents the running action on the P-h line chart of embodiment of the present invention 1.
Fig. 3 is the figure that represents the Temperature Distribution of cold-producing medium in the water heat exchanger of embodiment of the present invention 1 and water.
Fig. 4 is the figure that represents the recurrent state for expansion valve opening of embodiment of the present invention 1.
Fig. 5 is the figure of the variation of the each operation values for expansion valve opening, the heating efficiency that represent embodiment of the present invention 1, COP.
Fig. 6 is the figure of the variation of another the each operation values for expansion valve opening, the heating efficiency that represent embodiment of the present invention 1, COP.
Fig. 7 is the figure that represents the control flow chart of embodiment of the present invention 1.
Fig. 8 is the figure that represents the formation of the freezing cycle device of embodiment of the present invention 2.
Fig. 9 is the figure that represents the running action on the P-h line chart of embodiment of the present invention 2.
The explanation of symbol
1 compressor, 2 radiators (water heat exchanger), 3 expansion valves, 4 heat dumps (evaporimeter), 5 inner heat exchangers, 20 supplying hot water side pumps, 21 hot water reservoir, 22 utilize side pump, 23,24,25 open and close valves, 29 pressure fans, 30,31,32,33,41,42,52 temperature detecting units, 35,51 pressure sensing cells, 40 control device, 50 heat power supply devices, 60 hot water storage devices
Detailed description of the invention
The freezing cycle device of embodiment of the present invention 1 is described below.
Fig. 1 is the structure chart that represents the freezing cycle device of embodiment of the present invention.In the drawings, the freezing cycle device of present embodiment is for using carbon dioxide (to use below CO
2represent) as the hot water supply device of cold-producing medium, formed by heat power supply device 50, hot water storage device 60, control device 40 that they are controlled.In the present embodiment, although represent the example of hot water supply device, be not limited to this, also can be air conditioner.Equally, cold-producing medium is not limited to carbon dioxide, also can be HFC series coolant.
Heat power supply device 50 is made up of compressor 1, radiator (hereinafter referred to as " water heat exchanger ") 2, inner heat exchanger 5, decompressor 3 (hereinafter referred to as " expansion valve "), heat dump 4 (hereinafter referred to as " evaporimeter "), inner heat exchanger 5; This compressor 1 compresses cold-producing medium; This radiator 2 takes out the heat of the high-temperature high-pressure refrigerant that has been subject to compression in compressor 1; This inner heat exchanger 5 to from water heat exchanger 2 out cold-producing medium further carry out cooling; This decompressor 3 reduces pressure to cold-producing medium, can change aperture; The cold-producing medium evaporation that this heat dump 4 has made to be depressurized in expansion valve 3; This inner heat exchanger 5 is further to heating from evaporimeter 4 cold-producing medium out., the heat exchanger of inner heat exchanger 5 for making the cold-producing medium of export department of water heat exchanger 2 and the cold-producing medium of the export department of evaporimeter 4 carry out heat exchange.There is the pressure fan 29 of air being delivered to the outer surface of evaporimeter 4.In addition, there is the 6th temperature detecting unit 33 of the inlet temperature of the first temperature detecting unit 30 of the discharge temperature that detects compressor 1, the second temperature detecting unit 31 that detects the outlet temperature of water heat exchanger 2, the 5th temperature detecting unit 32 that detects the entrance refrigerant temperature of evaporimeter 4, detection compressor 1.And above-mentioned the first temperature detecting unit 30 and the second temperature detecting unit 31 are equivalent to respectively the first refrigerant condition detecting unit of the present invention and second refrigerant state detection unit in the control example of Fig. 7 described later.
Hot water storage device 60 is connected on the water heat exchanger 2 as radiator by pipe arrangement, by heat source side pump 20, hot water reservoir 21, utilize side pump 22, open and close valve 23,24,25 to form.Here, open and close valve 23,24,25 can be the simple valve that only carries out opening and closing operations, also can be the valve that can change aperture.The occasion having declined at the water level of hot water reservoir 21, open and close valve 24,25 is closed, open open and close valve 23, carries out water supply to be heated to the hot water storage running of set point of temperature.In addition, the occasion that wait in the winter time that radiation loss is large, temperature in hot water reservoir 21 has declined, open and close valve 23,25 is closed, and open and close valve 24 opens, carry out the circular heating running that again low-temperature water heating in hot water reservoir 21 boiled.In addition, in the time utilizing supplying hot water, open and close valve 23,24 is closed, open and close valve 25 is opened, and utilizes side pump 22 to move, by the delivery having stored to utilizing side.And, the 3rd temperature detecting unit 41 of the inlet temperature that detects heated medium (water) is installed at the entrance side of water heat exchanger 2, the 4th temperature detecting unit 42 of the outlet temperature that detects heated medium (water) is installed at the outlet side of water heat exchanger 2 in addition.
Fig. 2 is the P-h line chart of the recurrent state during the hot water storage of the freezing cycle device shown in key diagram 1 turns round.In Fig. 2, solid line represents the refrigerant condition under a certain expansion valve opening, and A, B, C, D, E, F represent the refrigerant condition in hot water storage running.In the time carrying out hot water storage running, the high-temperature high-pressure refrigerant (A) of discharging from compressor 1 flow into water heat exchanger 2.In water heat exchanger 2, cold-producing medium, on one side to the water-cooled circulating in hot water storage loop, reduces the temperature of self on one side, heats up thereby make to supply water.The cold-producing medium (B) having flowed out from water heat exchanger 2 dispels the heat inner heat exchanger 5, and temperature further reduces (C), is reduced pressure (D) by expansion valve 3, become low-temperature low-pressure refrigerant.Low-temperature low-pressure refrigerant is from air caloric receptivity in evaporimeter 4, and self evaporates (E).The cold-producing medium having flowed out from evaporimeter 4 is heated and is become gas (F) in inner heat exchanger 5, attracted to compressor 1, forms freeze cycle.
Here, expansion valve 3 for example, so that the suction degree of superheat of compressor 1 becomes the mode of desired value (5～10 DEG C) is controlled.Specifically, carry out according to the detected value of the 5th temperature detecting unit 32 of the entrance refrigerant temperature of detection evaporimeter 4 the temperature slippage that the pressure loss in modifying factor evaporimeter 4 and inner heat exchanger 5 causes, calculate evaporating temperature (ET), use the detected value (Ts) of the 6th temperature detecting unit 33 of the inlet temperature that detects compressor 1 to calculate and suck degree of superheat SHs by following formula.
SHs＝Ts-ET
According to above formula, so that SHs becomes the aperture of the mode control expansion valve 3 of desired value.And, although represented to calculate according to the detected value of the 5th temperature detecting unit 32 example of evaporating temperature (ET), but be not limited to this, pressure sensing cell (the second pressure sensing cell) 51 (with reference to Fig. 1) also can be set between the suction inlet that exports to compressor 1 from the low-pressure side of inner heat exchanger 5, obtain cold-producing medium saturation temperature from its detected value.In addition, from guaranteeing the viewpoint of equipment dependability, the function that the liquid that prevents compressor 1 is returned has precedence over turn round the well function of water heat exchanger 2 of efficiency, so, have precedence over other high efficiency running and control and suck degree of superheat control.
In Fig. 2, dot the action on the P-h line chart of occasion of the aperture that has reduced expansion valve 3.Reducing the occasion of aperture of expansion valve 3, the refrigerant flow that flow into evaporimeter 4 from expansion valve 3 reduces, and the suction degree of superheat of compressor 1 increases temporarily.In addition, cold-producing medium moves towards high-pressure side, so on high-tension side pressure rise, discharge temperature uprises.Accompany therewith, water heat exchanger outlet temperature declines, so that the temperature difference in water heat exchanger 2 becomes necessarily.If water heat exchanger outlet temperature declines, the heat exchange amount in inner heat exchanger 5 declines, result, and the state cardinal principle before sucking the degree of superheat and reducing the aperture of expansion valve 3 is identical, shows as certain value.That is, the aperture of expansion valve 3 changes by the variation of the heat exchange amount of inner heat exchanger 5 and is absorbed (heat exchange amount changes corresponding to the aperture of expansion valve 3), and the variation that makes to suck the degree of superheat is less.Therefore, only can not guarantee the heating efficiency of water heat exchanger 2 by controlling the suction degree of superheat of compressor 1, decrease in efficiency.Therefore, need to be to guarantee heating efficiency and to improve the new control of running efficiency as object.
Below, the reason in generation maximum aspect performance (COP) according to the Temperature Distribution explanation in the water heat exchanger shown in Fig. 3.
Fig. 3 is the figure that represents the Temperature Distribution of cold-producing medium in water heat exchanger 2 and water, in the drawings, thick solid line represents cold-producing medium, thin solid line represents the variations in temperature of water, Δ T1 represents the temperature difference of water heat exchanger inlet temperature and water outlet temperature, Δ T2 represents the temperature difference of water heat exchanger outlet temperature and water inlet temperature, Δ Tp represents that the temperature difference of cold-producing medium in water heat exchanger 2 and water becomes the temperature difference of minimum narrow point, and Δ T represents the temperature difference of water heat exchanger inlet temperature and water heat exchanger outlet temperature.As Fig. 4 with respect to as shown in the recurrent state of expansion valve opening, if reduce expansion valve 3 aperture, make discharge temperature rise, be under the condition that cardinal principle is certain in the heating efficiency of water heat exchanger 2, the outlet temperature of water heat exchanger 2 declines, with the cold-producing medium in maintenance water heat exchanger 2 and the mean temperature difference of water, in addition, the temperature difference Tp of narrow point also reduces.In addition, because refrigerant amount moves towards high-pressure side, so discharge pressure rises, input increases, and COP declines.On the contrary, if increase expansion valve 3 aperture, make discharge temperature decline, the outlet temperature of water heat exchanger 2 uprises, with the cold-producing medium in maintenance water heat exchanger 2 and the mean temperature difference of water, in addition, the temperature difference Tp of narrow point also increases, but because heating efficiency ratio diminishes, so also decline at this occasion COP.Therefore,, as dotted in figure, there is the suitable expansion valve opening that makes COP maximum.
Fig. 5 represents the variation of the operation values that the temperature of the each several part of the occasion having changed from the aperture of expansion valve 3 obtains.Fig. 5 represents the aperture (%) of expansion valve 3 with transverse axis, represent temperature difference T2, heating efficiency ratio, the COP ratio of the suction degree of superheat, discharge temperature, water heat exchanger outlet temperature with the water inlet temperature of compressor 1 with the longitudinal axis.Heating efficiency when COP represents by following ratio than all, and described ratio is to establish with respect to expansion valve opening to become the ratio that great value is 100% occasion.Can find out, change with respect to the aperture of expansion valve 3, the variation that sucks the degree of superheat can be regarded certain value substantially as, can not be judged the variation of heating efficiency ratio, COP ratio by the suction degree of superheat.Can find out, to COP controlled as maximum occasion according to the poor Δ T2 of discharge temperature, water heat exchanger outlet temperature and water inlet temperature as the conventional example, near COP as dotted in figure becomes maximum expansion valve opening, the variation of discharge temperature, temperature difference T2 is little, for COP is controlled as maximum, need high-precision temperature survey.
Fig. 6 represents the variation of another operation values that the temperature of the each several part of the occasion having changed from the aperture of expansion valve 3 obtains.Fig. 6 represents the aperture (%) of expansion valve 3 with transverse axis, represent gateway temperature difference Thx, the discharge temperature (water heat exchanger outlet temperature) and the poor Δ T of water heat exchanger outlet temperature, above-mentioned Δ T1 total temperature difference ∑ Δ T, heating efficiency ratio, the COP ratio with Δ T2 of inner heat exchanger with the longitudinal axis.The characteristic of Fig. 6 represents, by control the heat exchange amount of inner heat exchanger 5 according to the temperature difference Thx of inner heat exchanger gateway, or by control the heat exchange amount of water heat exchanger 2 according to the total temperature difference ∑ Δ T of Δ T1 and Δ T2, can COP become maximum near running.In addition, can learn, near that the temperature difference T of discharge temperature and water heat exchanger outlet temperature becomes maximum expansion valve opening at COP also significantly changes, if control according to temperature difference T, and can must be less by the peaked Deviation Control from COP., only represent the occasion of temperature difference T here, even but control according to temperature difference T1 and temperature difference T2 poor (Δ T1-Δ T2), also can bring into play same effect.
Like this, as the normal condition of water heat exchanger 2, adopt the high-pressure side outlet temperature of inner heat exchanger 5 in the occasion of Δ Thx, adopt discharge temperature in the occasion of Δ T, adopt discharge temperature and water side gateway temperature in the occasion of ∑ Δ T, thus near the running of that can implementation efficiency maximum.
In addition, can learn from Fig. 6, the total temperature difference ∑ Δ T of the temperature difference T2 of the temperature difference T1 of water heat exchanger inlet temperature and water outlet temperature and water heat exchanger outlet temperature and water inlet temperature becomes minimum, control the meaning that also has physics aspect according to this index, rational, but compared with temperature difference T, the variations in temperature that becomes near maximum at COP is little, needs high-precision temperature detection.In addition, can think according to Fig. 3, become maximum occasion at COP, the temperature difference Tp of narrow point and water heat exchanger outlet temperature equate substantially with the temperature difference T2 of water inlet temperature.This be because, consider from the characteristic of heat exchanger, in water heat exchanger 2, become 2 minimum temperature difference not to either party's skew and equal occasion can be brought into play maximum performance.Therefore, also can make Δ Tp and Δ T2 equally control expansion valve 3.
Below, by so that suck the degree of superheat and above-mentioned temperature difference T and converge the control action of the freezing cycle device of the example key diagram 1 of the mode control expansion valve opening of desired value.
Fig. 7 is the flow chart that represents the control action of freezing cycle device.In the present invention, from making the preferential object of product reliability, make the control ratio of the suction degree of superheat (SHs) of compressor 1 preferential for guaranteeing the control of temperature difference T of heating efficiency.
First, less of the occasion (S101) below predefined convergence range Δ SH than desired value (SHm) in the suction degree of superheat (SHs), expansion valve opening is declined, until suck the degree of superheat (SHs) convergence.Suck the degree of superheat (SHs) if guarantee like this, next make temperature difference T converge to desired value.Specifically, less of the occasion (S102) below predefined convergence range δ T than desired value (Δ Tm) at temperature difference T, expansion valve opening is declined, make temperature difference T convergence.Like this, the lower limit of the suction degree of superheat (SHs) and temperature difference T is suppressed.
Next, arrive greatly occasion (S103) more than predefined convergence range Δ SH than desired value (SHm) in the suction degree of superheat (SHs), expansion valve opening is increased, until suck the degree of superheat (SHs) convergence.Like this, if suck the degree of superheat (SHs) convergence, next make temperature difference T converge to desired value.Specifically, arrive greatly occasion (S104) more than predefined convergence range δ T at temperature difference T than desired value (Δ Tm), expansion valve opening is increased, make temperature difference T convergence.Like this, the higher limit of the suction degree of superheat (SHs) and temperature difference T is suppressed.And, although represented that preferential control sucks the example of the degree of superheat, use the occasion of the compressor with the endurance of returning with respect to liquid to be not limited to this, change priority and also can give play to same effect.By above control, make to suck the degree of superheat (SHs) and temperature difference T and converge to desired value.
In the above description, illustrate that the mode control to converge to desired value (SHm, Δ Tm) sucks the example of the degree of superheat (SHs) and temperature difference T, but also can use total temperature difference ∑ Δ T, the Δ T1 of Δ T1 and Δ T2 and Δ T2 poor (Δ T1-Δ T2) or Δ Thx to replace temperature difference T, so that its mode that converges to desired value is controlled.In the occasion that uses ∑ T and (Δ T1-Δ T2), obtain these values according to the detected temperatures computing of the first temperature detecting unit 30, the second temperature detecting unit 31, the 3rd temperature detecting unit 41 and the 4th temperature detecting unit 42.In addition, in the occasion that uses Δ Thx, export to from the high-pressure side of inner heat exchanger 5 between the entrance of expansion valve 3 inner heat exchanger outlet temperature detecting unit 52 (with reference to Fig. 1) is installed, according to the detected temperatures of the detected temperatures of the second temperature detecting unit 31 and inner heat exchanger outlet temperature detecting unit 52, obtain their temperature difference Thx.
Can learn according to above explanation, in the present embodiment, except the degree of superheat control that compressor sucks, also according to the temperature difference T of discharge temperature and water heat exchanger outlet temperature (or ∑ Δ T, Δ T1-Δ T2, Δ Thx), so that COP becomes maximum mode control expansion valve opening, so, can obtain high efficiency freezing cycle device.
In addition, according to the output of the 5th temperature detecting unit 32 or pressure sensing cell 51, obtain cold-producing medium saturation temperature (ET), then, detected temperatures (Ts) and cold-producing medium saturation temperature (ET) by the 6th temperature detecting unit 33 are obtained the suction degree of superheat (SHs), so that this suction degree of superheat (SHs) becomes the mode control expansion valve opening of desired value, so, can guarantee the degree of superheat of the sucting of compressor 1, can prevent that liquid from returning to compressor 1, can guarantee reliability.In addition, the example in the example of Fig. 1, the 5th temperature detecting unit 32 being located between expansion valve 3 and evaporimeter 4 is illustrated, but as long as the entrance from evaporimeter 4 is to the low-pressure side entrance of inner heat exchanger 5, also configurable in any position.
In addition, in the present embodiment, in the time controlling the degree of superheat and the above-mentioned temperature difference (Δ T, ∑ Δ T, Δ T1-Δ T2, Δ Thx), carry out the control of the degree of superheat in the mode of the control that has precedence over the above-mentioned temperature difference, also guaranteed the reliability of compressor 1 from this point.
In addition, in the present embodiment, radiator is made up of water heat exchanger, can obtain high efficiency hot water supply device.
The freezing cycle device of embodiment of the present invention 2 is described below.
Fig. 8 is the figure that represents the formation of freezing cycle device of the present invention.The points different from embodiment 1 are, the first temperature detecting unit 30 that the first pressure sensing cell 35 replaces the discharge temperature that detects compressor 1 is set.Obtain and become the imaginary saturation temperature of the normal condition of water heat exchanger 2 (following, to be called imaginary saturation temperature) according to this first pressure sensing cell 35.In addition, the pressure sensor that this first pressure sensing cell 35 for example can arrange with abnormal ascending in order to prevent high pressure shares.Running action is identical with embodiment 1, so description thereof is omitted.
In the present embodiment, same with HFC series coolant in the past, calculate the imaginary supercooling degree that water heat exchanger 2 exports, control the refrigerant condition that water heat exchanger 2 exports.Specifically, the first pressure sensing cell 35 arranging from substituting the first temperature detecting unit 30, obtain the normal condition of imaginary saturation temperature as water heat exchanger 2, poor from the outlet temperature Tcout of imaginary saturation temperature Tsat and the water heat exchanger 2 that detected by the second temperature detecting unit 31, obtain imaginary supercooling degree (following, to be called imaginary supercooling degree SC) by following formula.
SC＝Tsat-Tcout
In the present embodiment, similarly control the aperture of expansion valve 3 with the occasion of the flow chart of Fig. 7, so that the SC having been obtained by above-mentioned calculating formula becomes the desired value (SCm) of efficiency maximum.
The method of obtaining of imaginary saturation temperature here, is described.
Fig. 9 is same with Fig. 2, is the figure that represents that on P-h line chart the running of freezing cycle device of the present invention is moved.As imaginary saturation temperature, if make pseudocritical temperature track, the dotted line イ of the such isothermal flex point of connection of dotted line ア such be the definition clear-cuts such as the vertical line that necessarily extends by the enthalpy of critical point, can freely set.But,,, as illustrated before this, should select near the temperature difference of maximal efficiency and become large such imaginary saturation temperature by maximal efficiency running freezing cycle device for stably.Now, imagination saturation temperature puts the isobaric line of force at pressure place and the intersection point of dotted line ア of B as the detected value of the first pressure sensing cell 35, or obtains as the isobaric line of force at pressure place and the intersection point of dotted line イ that the detected value of the first pressure sensing cell 35 puts B.
In the present embodiment, use imaginary saturation temperature to replace the discharge temperature of compressor 1, so, can omit the first temperature detecting unit 30 of Fig. 1, can realize cost degradation.In addition, same with HFC series coolant in the past, control the supercooling degree that water heat exchanger 2 exports, so, the control that can directly use the expansion valve in the past using.
Claims (10)
1. a freezing cycle device, at least comprise decompressing unit, heat dump, inner heat exchanger that compressor, radiator, aperture can change, this inner heat exchanger makes the cold-producing medium of above-mentioned radiator outlet portion and the cold-producing medium of above-mentioned heat dump export department carry out heat exchange; It is characterized in that:
There is the first temperature detecting unit detecting from the refrigerant temperature between the entrance that exports to above-mentioned radiator of above-mentioned compressor, and detection is from the second temperature detecting unit of the refrigerant temperature between the high-pressure side entrance that exports to above-mentioned inner heat exchanger of above-mentioned radiator
So that becoming COP, the temperature difference of the detected temperatures of the detected temperatures of above-mentioned the first temperature detecting unit and above-mentioned the second temperature detecting unit (Δ T) is set to the aperture of the above-mentioned decompressing unit of mode control of maximum desired value.
2. a freezing cycle device, at least comprise decompressing unit, heat dump, inner heat exchanger that compressor, radiator, aperture can change, this inner heat exchanger makes the cold-producing medium of above-mentioned radiator outlet portion and the cold-producing medium of above-mentioned heat dump export department carry out heat exchange; It is characterized in that:
Have detect refrigerant temperature between the entrance that exports to above-mentioned radiator of above-mentioned compressor the first temperature detecting unit, detect the refrigerant temperature between the high-pressure side entrance that exports to above-mentioned inner heat exchanger of above-mentioned radiator the second temperature detecting unit, detect by the 3rd temperature detecting unit of the inlet temperature of the heated medium of the heat exchange heating above-mentioned radiator and detect the 4th temperature detecting unit by the outlet temperature of the above-mentioned heated medium of above-mentioned radiators heat
So that poor (the Δ T1-Δ T2) of the 3rd temperature difference (Δ T2) of second temperature difference of the detected temperatures of the detected temperatures of above-mentioned the first temperature detecting unit and above-mentioned the 4th temperature detecting unit (Δ T1) and the detected temperatures of above-mentioned the second temperature detecting unit and the detected temperatures of above-mentioned the 3rd temperature detecting unit becomes the aperture of the above-mentioned decompressing unit of mode control of desired value.
3. a freezing cycle device, at least comprise decompressing unit, heat dump, inner heat exchanger that compressor, radiator, aperture can change, this inner heat exchanger makes the cold-producing medium of above-mentioned radiator outlet portion and the cold-producing medium of above-mentioned heat dump export department carry out heat exchange; It is characterized in that:
There is the first pressure sensing cell detecting from the refrigerant pressure between the above-mentioned decompressing unit entrance of exporting to of above-mentioned compressor, and detection is from the second temperature detecting unit of the refrigerant temperature between the high-pressure side entrance that exports to above-mentioned inner heat exchanger of above-mentioned radiator
So that become the mode of desired value according to the operation values of the detected temperatures computing of the detected pressures of above-mentioned the first pressure sensing cell and above-mentioned the second temperature detecting unit, control the aperture of above-mentioned decompressing unit.
4. a freezing cycle device, at least comprise decompressing unit, heat dump, inner heat exchanger that compressor, radiator, aperture can change, this inner heat exchanger makes the cold-producing medium of above-mentioned radiator outlet portion and the cold-producing medium of above-mentioned heat dump export department carry out heat exchange; It is characterized in that:
There is the second temperature detecting unit detecting from the refrigerant temperature between the high-pressure side entrance that exports to above-mentioned inner heat exchanger of above-mentioned radiator, and detect the inner heat exchanger outlet temperature detecting unit that exports to the refrigerant temperature between the entrance of above-mentioned decompressing unit from the high-pressure side of above-mentioned inner heat exchanger
So that the temperature difference (Δ Thx) of the detected temperatures of the detected temperatures of above-mentioned the second temperature detecting unit and above-mentioned inner heat exchanger outlet temperature detecting unit becomes the aperture of the above-mentioned decompressing unit of mode control of desired value.
5. according to the freezing cycle device described in any one in claim 1～4, it is characterized in that: have and detect the 6th temperature detecting unit that exports to the refrigerant temperature between the suction inlet of above-mentioned compressor from the low-pressure side of above-mentioned inner heat exchanger,
Calculate the degree of superheat of compressor sucting according to the detected temperatures of the cold-producing medium saturation temperature at the detection position of above-mentioned the 6th temperature detecting unit and above-mentioned the 6th temperature detecting unit, so that the above-mentioned degree of superheat becomes the aperture of the above-mentioned decompressing unit of mode control of desired value.
6. freezing cycle device according to claim 5, it is characterized in that: between the suction inlet that exports to above-mentioned compressor from the low-pressure side of above-mentioned inner heat exchanger, the second pressure sensing cell is set, obtains above-mentioned cold-producing medium saturation temperature according to the detected value of above-mentioned the second pressure sensing cell.
7. freezing cycle device according to claim 5, it is characterized in that: to the low-pressure side entrance of above-mentioned inner heat exchanger, the 5th temperature detecting unit is set at the entrance from above-mentioned heat dump, obtains above-mentioned cold-producing medium saturation temperature according to the detected temperatures of above-mentioned the 5th temperature detecting unit.
8. freezing cycle device according to claim 5, is characterized in that: for the aperture control of above-mentioned decompressing unit, preferentially carry out the control of the above-mentioned degree of superheat than the control of the temperature difference.
9. according to the freezing cycle device described in any one in claim 1～4, it is characterized in that: above-mentioned radiator is water heat exchanger.
10. according to the freezing cycle device described in any one in claim 1～4, it is characterized in that: use carbon dioxide as cold-producing medium.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2007310097A JP4948374B2 (en) | 2007-11-30 | 2007-11-30 | Refrigeration cycle equipment |
| JP2007-310097 | 2007-11-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2008801141141A Division CN101842645B (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
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| CN102425872A CN102425872A (en) | 2012-04-25 |
| CN102425872B true CN102425872B (en) | 2014-06-25 |
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| CN2008801141141A Active CN101842645B (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
| CN201110289736.1A Active CN102425872B (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
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| CN2008801141141A Active CN101842645B (en) | 2007-11-30 | 2008-11-20 | Refrigeration cycle device |
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| EP (5) | EP2647927B1 (en) |
| JP (1) | JP4948374B2 (en) |
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|---|---|
| DK2196745T3 (en) | 2017-12-11 |
| CN101842645A (en) | 2010-09-22 |
| ES2605462T3 (en) | 2017-03-14 |
| EP2196745B1 (en) | 2017-11-08 |
| EP2647927A3 (en) | 2015-07-29 |
| JP4948374B2 (en) | 2012-06-06 |
| EP2196745A1 (en) | 2010-06-16 |
| EP2647925B1 (en) | 2016-12-21 |
| EP2647928A3 (en) | 2015-08-05 |
| EP2647926A3 (en) | 2015-07-29 |
| ES2700938T3 (en) | 2019-02-20 |
| CN102425872A (en) | 2012-04-25 |
| EP2647926B1 (en) | 2018-10-24 |
| DK2647926T3 (en) | 2019-01-07 |
| EP2647927A2 (en) | 2013-10-09 |
| EP2647925A3 (en) | 2015-08-05 |
| EP2647927B1 (en) | 2020-09-16 |
| EP2647928B1 (en) | 2016-10-26 |
| ES2823758T3 (en) | 2021-05-10 |
| EP2647926A2 (en) | 2013-10-09 |
| US20100205987A1 (en) | 2010-08-19 |
| CN101842645B (en) | 2012-11-28 |
| DK2647928T3 (en) | 2016-12-12 |
| DK2647925T3 (en) | 2017-02-06 |
| ES2611980T3 (en) | 2017-05-11 |
| EP2647925A2 (en) | 2013-10-09 |
| WO2009069524A1 (en) | 2009-06-04 |
| ES2650233T3 (en) | 2018-01-17 |
| EP2196745A4 (en) | 2013-02-13 |
| JP2009133547A (en) | 2009-06-18 |
| EP2647928A2 (en) | 2013-10-09 |
| DK2647927T3 (en) | 2020-10-19 |
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